CN105546034A - Impeller type inertia and damping device - Google Patents

Abstract

The invention discloses an impeller-type inertial and damping device, which belongs to the field of mechanical force control. The device in the invention includes an impeller rod, a hydraulic cylinder, a mass impeller, a rolling bearing, a free piston, an air chamber, an upper hanging ear and a lower hanging ears; the hydraulic cylinder is provided with an impeller rod, and the impeller rod is connected to the mass impeller through a rolling bearing; the mass impeller can rotate around the impeller rod with the flow of the oil, and convert part of the kinetic energy of the oil into the kinetic energy of the impeller . The invention integrates the inertial device and the damping device into an integrated mechanism, which effectively reduces the structural complexity of the force control system and reduces the space occupancy rate; at the same time, the response speed of the integrated device is better than other split devices. Compared with the prior art, the present invention has the advantages of good vibration isolation effect, high degree of component integration, fast response, high reliability, less movable parts, easy installation and layout, space saving of vibration isolation system, cost saving, high production efficiency, etc. .

Description

An impeller type inertial and damping device

technical field

The invention belongs to the field of mechanical force control, in particular to the field of force control equipment using dynamic vibration absorption. The present invention relates to a device for controlling mechanical force (such as vibratory force), especially an impeller type inertial and damping device.

Background technique

Mechanical structures and systems will inevitably vibrate during motion. For complex structures and systems, only relying on optimal design cannot solve the vibration problem. Therefore, the use of force control equipment is an important and effective vibration isolation method, which can Used in many fields, such as vehicle vibration isolation, bridges, building vibration isolation, etc.

The vibration isolation system based on the traditional vibration isolation theory cannot solve the contradiction between the excellent vibration isolation effect and the equipment working space and dynamic load. The vibration isolation effect is not ideal, which hinders the further development of vibration isolation technology. According to the electromechanical similarity theory, the force flow in the mechanical system corresponds to the current in the electrical system, and the speed in the mechanical system corresponds to the voltage in the electrical system. The force phase of the two ends of the spring lags behind the velocity phase of the two ends, the force phase of the two ends of the damping device is always the same as the velocity phase of the two ends, and the force phase of the two ends of the force control device is ahead of the velocity phase of the two ends. Based on the above conclusions, an inertial device is added to the original spring and damper structure to realize a dynamic vibration-absorbing vibration-isolation structure that can buffer and attenuate high-frequency vibrations and impacts, as well as low-frequency vibrations and impacts.

At present, the force control equipment using dynamic vibration absorption has various forms of equipment structures such as rack and pinion type, ball screw, hydraulic power generation type, lever mass type, torsion type, planetary gear type with small tooth difference, and cycloidal steel ball type. However, there are quite a lot of moving parts in these force control devices using dynamic vibration absorption, which makes the mechanism processing process complicated, the manufacturing cost is high, and it is not easy to arrange in practice, and there is more friction between the parts, resulting in the vibration isolation effect of the final mechanism There is still a certain gap with the expected effect.

Chinese patent CN201110360046.0 proposes an integrated shock absorber in which an inerter and a damper are coaxially connected in parallel. The flywheel is installed on the hydraulic cylinder, making the overall height of the mechanism larger and difficult for actual arrangement; Chinese patent CN201210107000.2 The proposed shock absorber device in which the inertial container and damping are connected in parallel, the flywheel is placed outside the hydraulic cylinder and needs to be connected by pipelines, which occupies a large space and the corresponding speed is relatively slow; Chinese patent CN201410721244.9 proposes an inertial The capacity and damping integrated gas shock absorber has a simple structure and fewer components, but compared with the present invention, there are more parts such as metal spiral tubes.

Contents of the invention

Aiming at the deficiencies of the prior art, the present invention provides an impeller-type inertial and damping device, the inertial device is integrated into the damping device, the number of moving elements of the device is significantly reduced, and the mass element is integrated into the damping device, reducing the The layout space can effectively solve the existing problems of complex structure of the vibration isolation system with inertial mass elements, large layout space required, short service life of the mechanism, and difficulties in processing and installation.

The present invention achieves the above-mentioned technical purpose through the following technical means.

An impeller type inertial and damping device includes an impeller rod, a hydraulic cylinder barrel, a mass type impeller, a rolling bearing, a free piston, an air chamber, an upper lug and a lower lug.

The hydraulic cylinder is provided with an impeller rod, and the impeller rod is connected with the mass impeller through a rolling bearing, and the mass impeller can rotate around the impeller rod in the axial direction; the top of the impeller rod is welded with an upper lug, and the impeller rod There is a free piston under the bottom of the hydraulic cylinder; the free piston separates the hydraulic cylinder from the air chamber during the up and down movement; the bottom of the hydraulic cylinder is welded with lower lifting lugs.

Further, the material of the mass impeller is metal or special plastic or special ceramic.

Further, one or more mass impellers may be arranged at a certain interval on the impeller rod.

Furthermore, ordinary shock absorber oil or magneto-rheological fluid is installed in the hydraulic cylinder to realize the controllability of the damping coefficient and the inertial coefficient.

Still further, the arrangement of the impeller-type inertial and damping equipment may be single-tube, double-tube or multi-tube.

The beneficial effect that the present invention can reach is:

1. The integrated layout of inertial equipment and damping equipment realized by the present invention can effectively reduce the space occupied by the vibration isolation system and facilitate the layout, and the response speed of the integrated equipment is better than that of the split structure, that is, it can Faster absorption of mechanical vibration is of great significance for the integration and weight reduction of equipment.

2. The present invention makes the structure more compact by integrating the two elements of the inertial device and the damping device, and at the same time the failure rate will be correspondingly reduced, which solves the problem that the structure of the existing vibration isolation system containing dynamic vibration absorbing components is too complicated, and the processing and installation Difficulty, high production cost and low production efficiency, the device has stronger practicability.

Description of drawings

Fig. 1 is the structural representation of a kind of impeller type inertial and damping equipment of the present invention;

Fig. 2 is the engineering schematic diagram of a kind of impeller type inertial and damping equipment of the present invention;

Fig. 3 is the front view of the mass impeller of the present invention;

Fig. 4 is a top view of the mass impeller of the present invention.

In the figure: 1-impeller rod; 2-hydraulic cylinder; 3-mass impeller; 4-rolling bearing; 5-free piston; 6-air chamber; 7-upper lug; 8-lower lug; 9-dust cover ; 10 - sealing assembly.

detailed description

The present invention will be further described below in conjunction with the accompanying drawings and specific embodiments, but the protection scope of the present invention is not limited thereto.

An impeller-type inertial and damping device can be arranged in a single-tube, double-tube or multi-tube type; the present invention is preferably a single-tube impeller-type inertial and damping device.

As shown in Figure 1, a schematic structural diagram of an impeller-type inertial and damping device, including an impeller rod 1, a hydraulic cylinder 2, a mass impeller 3, a rolling bearing 4, a free piston 5, an air chamber 6, an upper lug 7 and a lower hanger ear 8;

The hydraulic cylinder 2 is provided with an impeller rod 1, and the impeller rod 1 is connected to the mass impeller 3 through a rolling bearing 4. The mass impeller 3 can rotate around the impeller rod 1 in the axial direction to generate inertial force, replacing the traditional The flywheel forms the force control device of the present invention; the top of the impeller rod 1 is welded with an upper lug 7, and the bottom of the impeller rod 1 is provided with a free piston 5, and the free piston 5 is a rubber with a certain thickness. The finished cylinder; the free piston 5 separates the hydraulic cylinder 2 from the air chamber 6 during the up and down movement; the bottom of the hydraulic cylinder 2 is welded with lower lifting lugs 8 .

The material of the mass impeller 3 is preferably metal, and special plastics or special ceramic materials can be used in some working environments with strong corrosion or other special requirements.

One or more of the mass impellers 3 can be arranged at a certain distance on the impeller rod 1. In Figure 1, the multi-impeller method is adopted, and the number of impellers can be increased or decreased according to different models, so that the equipment can obtain the best inertial mass coefficient, so that the vibration isolation system can exert the maximum vibration isolation effect.

The mass impeller 3 is an impeller mechanism with non-negligible mass. The mass impeller 3 rotates with the impeller rod as the axis along with the flow of the liquid in the hydraulic cylinder 2 to generate an inertial force, thereby storing a part of the kinetic energy and acting as an inertial force. The effect of the mass element replaces the traditional flywheel well, forming a mass impeller type force control device; changing the parameters of the mass type impeller 3 can change the inertia coefficient of the mass type impeller 3 and the damping coefficient of the equipment of the present invention .

The hydraulic cylinder 2 is preferably ordinary shock absorber oil, which is used to realize the controllability of the damping coefficient and the inertial coefficient; the hydraulic cylinder 2 of the present invention can also be equipped with magnetorheological fluid (MR). Rheological fluid (MR) is a liquid containing suspended high-density iron ions, and the viscosity of the liquid can be adjusted by applying an external magnetic field; when the magnetic field environment around the magnetorheological fluid is changed, the inertia of the mass impeller 3 can be changed coefficient and the damping coefficient of the device of the present invention.

The air chamber 6 is filled with nitrogen or air, which acts as a gas-filled shock absorber, which can not only reduce the volume difference caused by the displacement of the impeller rod 1, but also make the hydraulic cylinder 2 work more stably.

In addition, the present invention can also adjust the number of mass impellers 3 by adding a control device, so as to realize controllable damping coefficient and inertia coefficient. At the rolling bearing 4, a controller (such as a solenoid valve) can be set to control the rotation of the mass type impeller 3. The present invention preferably adopts a solenoid valve control. When the solenoid valve is closed, the mass type impeller 3 can rotate; when the solenoid valve is opened, The mass impeller 3 cannot rotate or can only partially rotate, so as to adjust the damping coefficient and the inertia coefficient.

In actual arrangement, an impeller-type inertial and damping device according to the present invention needs to be used in parallel with spring elements (≥1) to form a vibration isolation system to prevent the vibration isolation device from being crushed by the gravity of the vibration isolation device and cause Breakdown, loss of vibration isolation function.

Fig. 2 is an engineering schematic diagram of an impeller type inertial and damping equipment, in which the dustproof cover 9 can play a dustproof role in actual use and prolong the service life of the equipment; the sealing assembly 10 is to prevent the oil from impeller rod 1 and The hydraulic cylinder 2 is leaking at the contact point. In the figure, by arranging the mass impeller 3 in the hydraulic cylinder 2, the structural design that the mass impeller 3 is connected to the impeller rod 1 through the rolling bearing makes the mass impeller 3 act as the flow valve of the damping device and the storage of the inertial device at the same time. energy components. Integrating the mass element into the damping element can effectively reduce the space occupied by the equipment and facilitate the layout. At the same time, the response speed of the integrated equipment is better than that of the split structure, that is, it can absorb mechanical vibration faster. For vibration isolation The integration and lightweight of equipment are of great significance.

Fig. 3, 4 are respectively the front view and the top view of the mass type impeller 3 of the present invention; the cross-sectional area of the mass type impeller 3 is S, then Wherein D is the diameter of the mass type impeller 3, and d is the diameter of the impeller rod 1;

The inertia coefficient of mass impeller 3 can be expressed as:

$\mathrm{<span\; class="notranslate">\; b</span>}<span\; class="notranslate">\; =</span>\mathrm{<span\; class="notranslate">\; \&eta;J</span>}{<span\; class="notranslate">\; (</span>\frac{\mathrm{<span\; class="notranslate">\; S</span>}}{\mathrm{<span\; class="notranslate">\; \&mu;</span>}}<span\; class="notranslate">\; )</span>}^{\mathrm{<span\; class="notranslate">\; 2</span>}}<span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; 1</span>}<span\; class="notranslate">\; )</span>$

In the formula, η is the transmission efficiency, J is the moment of inertia of the impeller, and μ is the ratio of the flow through the impeller to the angular velocity of the impeller.

Formula (1) shows that by selecting the appropriate parameters such as impeller geometric size, mass, and number of impeller blades, the inertia coefficient of the mass-type impeller that can meet the requirements can be designed to control the mechanical force. The height parameter H in Figure 3 can be selected according to the parameters of the rolling bearing.

The working process of the device will be further explained below.

The upper lug 7 on the top of the impeller rod 1 is connected to the vibration generating source, the lower lug 8 on the bottom of the hydraulic cylinder 2 is connected to the vibration isolation equipment, and the impeller type inertial and damping equipment is connected in parallel with a spring element. When vibration occurs, the vibration force acts on the impeller rod 1, and drives the mass impeller 3 to move in the hydraulic cylinder 2. When the oil flows through the mass impeller 3, it pushes it to rotate around the impeller rod 1, resulting in an inertial energy storage effect , that is, the vibration energy is converted into the kinetic energy of impeller rotation and stored. Since the impeller rod 1 enters the hydraulic cylinder 2 to reduce the cylinder area, the air chamber 6 is set to compensate, and the liquid inside the hydraulic cylinder 2 exerts pressure on the free piston 5, thereby compressing the gas in the air chamber 6, so that Its volume is reduced to compensate for the volume of impeller rod 1 entering hydraulic cylinder barrel 2 . When it is necessary to control the parameters of the vibration isolation equipment, it can be realized by controlling the switch of the solenoid valve; when the solenoid valve is closed, the mass impeller 3 can rotate; when the solenoid valve is opened, the mass impeller 3 cannot rotate or only partly can rotate.

The impeller type inertial and damping device of the invention can be used for vibration reduction in many fields such as vehicles, engineering machinery, bridges, buildings, and helicopter propellers.

The described embodiment is a preferred implementation of the present invention, but the present invention is not limited to the above-mentioned implementation, without departing from the essence of the present invention, any obvious improvement, replacement or modification that those skilled in the art can make Modifications all belong to the protection scope of the present invention.

Claims (5)

1. A kind of impeller type inertial and damping equipment is characterized in that, comprises impeller rod (1), hydraulic cylinder barrel (2), mass type impeller (3), rolling bearing (4), free piston (5), air chamber ( 6), the upper lug (7) and the lower lug (8); The hydraulic cylinder (2) is provided with an impeller rod (1), and the impeller rod (1) is connected to the mass impeller (3) through a rolling bearing (4), and the mass impeller (3) can be axially Rotate around the impeller rod (1); the top of the impeller rod (1) is welded with upper lugs (7), and the bottom of the impeller rod (1) is provided with a free piston (5); the free piston (5) In the process of moving up and down, the hydraulic cylinder (2) is separated from the air chamber (6); the bottom of the hydraulic cylinder (2) is welded with lower lifting lugs (8). 2. The impeller type inertial and damping device according to claim 1, the material of the mass type impeller (3) is metal or special plastic or special ceramic. 3. The impeller type inertial and damping device according to claim 1, one or more mass impellers (3) can be arranged at a certain interval on the impeller rod (1). 4. A kind of impeller type inertial and damping equipment according to claim 1, common shock absorber oil or magneto-rheological fluid is housed in the described hydraulic cylinder barrel (2), for realizing the adjustable damping coefficient and inertial coefficient. control. 5. The impeller-type inertial and damping device according to claim 1, its arrangement can be single-tube, double-tube or multi-tube.